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C. M. MANLY..

VARIABLE SPEED TRANSMITHQG MECHANISM. nrucmou mm ocr. at. 1901,

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Patented Oct. 7, 1919.

C. M. MANLY.

VARIABLE SPED TRANSMITTING MECHANISM.

APPLICATION FILED oct. 31. I901.

1,317,? 19. Patented Oct. 7,1919.

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C. M. MANLY.

VARIABLE SPEED TRANSMITTING MECHANISM.

APPLICATION HLED OCT. 3|. 1901. 1,317,719. Patented 0%. 7,1919.

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C. M. MANLY.

VARIABLE smo TRANSMITTING MECHANISM.

APPLICATION FlLiD OCT. 3|. 1901. 1,317,719. Patented Oct. 7,1919.

9 SHEETS-SHEET 4 Inventor:

I Y A 4- C. M. MANLY. mm smo IBANSMl-TIING MECHANISM.

1,317,719. Patented Oct. 7,1919.

9 SHEETS SHE ET 5- C. M. MANLY.

VARIABLE SPEED TRANSMITTING MECHANISM.

APPLICATION FILED OCT. 3t. 1901. 1,317,719. Patented Oct. 7,1919.

9 SHEETS-SHEET 6 /n. m I it c- M! VARIABLE SPEED TRANSMITI'ING MECHANISM.

APPLICATION FILED OCT. .1907.

- Patented Oct. 7,1919.

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c. M. MANLY.

VARIABLE SPEED TRANSMHTING MECHANISM.

V 7 APPLICATION FILED OCT. 3|. I907- 1,317,719, Patented Oct. 7,1919.

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Inventor: W by v GZh/" M C. M. MANLY.

VARIABLE SPEED mmsmmme MECHANISM.

APPLICATION mm 001.31. 190:.

1,317,719., v Patented Oct. 7,1919.

9 SHEETS-SHEET 9- the motor when the are revolvm GHABLES M. MANLY, OF NEW YORK, N. Y.

VARIABLE-SPEED-TEANSMITTING MECHANISM- Specification of Letters Patent.

Patented Oct. v, 1919.

Application filed October 31, 1907. Serial No. 399,989.

To all whom it may concern:

Be it known that I, CHAnLEs M. MANIA, a citizen of the United States, residing in the city of New York, count and State of New York, have invented certain new and useful Improvements in VariablB-Speed-Transmitting Mechanism, of which the following is a specification.

My resent invention is an improvement in variable speed transmitting mechanisms of the class shown and described in in Letters Patent No. 710,485, dated Octo er 7, 1902 and No, 801,097, dated October 3, 1905, in w ich a pumping device and a motor oporated by fluid delivered fromthe pump, are interposed between a prime mover and a driven device, whereby the driven device may be caused to operate at any and all speeds in both directions with a torque inversely proportional to its speed, without re quiring changes either in the speed, direction of rotation, or power of the prime mover, I

One object of my invention is to provide improved, simple and effective means in such mechanisms for varyingflat will the velocity ratio of the driven device to the primemover; a further object is to pro-.

vide means whereby, whenthe pump and motor shafts are revolving in the same direction at substantially the same speed, the said shafts will be automatically locked toget-her and when they cease to revolve at equal speeds will be automatically unlocked.

With these and other objects in view. my invention consists of an improved speed transmitting mechanism embodying a pump driven from any external source of'power a motor onnected to the pump by a flui' and 3.119. ted to be connected to adriven device an means for adjusting the relativecapacities of the pump and them otor, as hereinafter more particularly pointed" out in the Iaiin-S 'andit further consists in means'for loc ing tegetherthe pump and at the same speed in the same direction, an finally, in the novel construction anddetails hereinafter described, with reference to the accompanyin drawings and more particularly pointe out in the claims.

'In the drawings, illustrating a preferred form in which my invention maybe" carried Out!" Fi re 1 is a partial longitudinal sections view through the pump;

' line 12 12, Fig.

Fig. 2 is a longitudinal sectional view through the motor;

Fi 3 is a transverse sectional view on the line 3-3, Fig. 1, looking in the direction of the arrows;

Fig. 4 is a partial transverse sectional view on the line 4-4, Fig. 1, looking in the direction of the arrows;

Fig. 5 is a partial transverse sectional view on the broken line 55, Fig. 1, lookmg in the direction of the arrows;

Fig. 6 is a side elevation of the main valve of the pump hereinafter referred to;

Fi 7 is an enlarged sectional view on the line 77, Fig. 1, looking in the direc tion of the arrows;

Figs 8, 9 and 10 illustrate on a smaller scale, the parts of Fig. 7 in different rel ative positions as hereinafter more fully de scribed;

Fi 11 is a transverse sectional view on the line 1111, Fig. 1, looking in the direction of the arrows;

Fig. 12 is a partial sectional view on the Fig. 13 is a si elevation of Fig. 12 looking in the direction of the arrow 13;

Figs. 14, 15, 16 and 17 are detail views of Fig. 12, hereinafter more particularly referred to;

Fig. 18, Sheet 3, is a central longitudinal sectional view on a larger scale of part of the left hand end of Fig. 1;

F1g. 19, Sheet 3, is a transverse sectional vlew on the line 19, Fig. 18, looking in the direction of the arrow;

Fig. 20 is a sectional view on a larger scale of certain control valves shown in elevation in Fig. 1

Fig. 21 is a sectional plan view on the line 21+21, Fig. 20, looking in the direction of the arrows;

Fig.- 22 is a sectional elevation on the line 22+22, Fig. 21';

same or corresprmding parts in all the views, the nun'icral 30 indicates the main pump castin g comprising throe radli'alcylinders, 31, Z2, and 33, arranged cquidistantly around the central crank chamber 34, the solid cy iinders being provided with ports 35, 36 and 37. respectively, connecting them to the central crank chamber 34, see Figs. 1, 3 and 5. Journaled in bearings 38 and 39 is a crank shaft 40 embodying a crank pin 41 providtul with a bushing 42, on the exterior of which is mounted a bushing 43, for convenience dcs inatcd the eccentric bush, the bore of which has an eccentricity, in respect to the outer circumference of the bush, equal to the eccentricity of the crank pin 41 with respect to the crank shaft 40. Rotatablmounted on the eccentric bush 43 are ,pitman 1 0019454, 45 and 46 connected by the pins 47, 48 and 49, respectively, to pistons 50, 51 and 52 slidably mounted in pump cylinders 31, 32 and 33, respectively. ll hen the eccentric bush i3 is maintained in such a position on the crank pin 4-1 that its outercircumference is eccentric to the crank shaft 10, rotation of said crank shaft 4-0 causes the pistons 50, 51 and to reciprocate in their respective cyl indcrs 31, and 33, the pitlnan rods 44, 45 and 46 being confined in their hearings on the eccentric bush -13 by annular rings 53 and 51, the former of which is integral with the left hand end of the eccentric bush 43, while the latter is connected to the night hand end of the said eccentric bush 43 by means of a pin 55 seated in a hole in said bush l3 and engaging a recess in said ring 5%, as shown in Fig. 1. hen the pistons 50, and 52 are thus reciprocated they draw in fluid on their inner strokes and force it out on their outer strokes through their respective ports 35, 36 and 37, the ingress and egress of such fluid being controlled *by a main rotary valve 56 mounted in the bore of the crank chamber 34. This valve 56 is provided with two ports 57 and 58. W'ith theports in themolativepositions shown in the drawings and assuming the crank shaft 40 to revolve in a clockwise direction as viewed from the left hand end of Fig. 1, the inlet port is 57 and the outletport is 58, the inlet iport 57 being at all times during the rotation Of'the valve connected, through the channel 59 formed in the interior of the valve, with the :inlet pipe 60, while the said outlet ,port-58'is similarly connected at all times through its channel 61 with the outlet pipe 62, the valve 56 being maintained in its :properqcosition, with respect to the crank pin a l, for ithe proper ingress and egress of fluid by suitable connections, hereinafter described, be tween the eccentric bush and thesaid valve 56. The inlet and outlet ports 57 and'58, respectively, of the main valve-56 are diametrically opposite (Fig. 5) being separated by a central web 350 which at diametrically opposite points broadens out into two bridges 351 and 352, respectively, each of which is of a circumferential width equal to the circumferential width of the ports 35, 36 and 3 7 leading from their respective cylinders. In Figs. 1 and 5, the main valve 56 is shown in such a position that the said bridge 351 just completely closes the port leading from the cylinder 31. the port 36 leading from the cylinder 32 being connected to the outlet port 58 while the port 37 lead ing from the cylinder 33 is connected to the inlet port 57, the lower bridge 352 of the valve, being midimy between the cylinder ports and 37, and since the piston 50 is at the upper end of its stroke where there is momentarily neither ingress nor egress of fluid, its from both ports of the valve. When the crank shaft -10 is rotated as above, the port 57 being the inlet port and the port 58 the outlet port, it .is evident that immediately that the valve is displaced from the position there shown, the port 35 becomes connected to the inlet port 57 of the valve whereby fluid is free to pass from the inlet pipe 60 through the channel 59 into the port 35 until the ,piston 50 reaches the lower end of its stroke, and since such motion of the piston occupies one-half revolution of the crank shaft it is readily seen that, if "the valve has been rotated simultaneously through 180 degrees, the port 35 at this moment will be cut oif from communication with the inlet port 57 and be prevented from communicating with the outlet port 58 from the fact that the said port 35 is just covered by the bridge 352 of the valve. Similarly during the outward stroke of the piston 50 the port 58 of the valve will be maintained in communication with the port 35, until the moment the piston reaches the outer end of its stroke when the valve reaches the position shown in the drawings where the port 35 is again out off by the bridge 351. In a correspondingmanner the ports 36 and 37 are maintained in communication with the inlet port 57 of the valve during the inward strokescftheirrespectivepistons 51 and 52, and with the outlet port-58 during the'outward -strokes, cne valve thereby serving to control the fluid ;passing in and out of all the cylinders. The inlet channel 59 is always :incommunication with the inlet pipe 60 and the outlet channel 61 is always in communication with the outletypipe 62, and so far as fluid pressure in these two channels iscon cerned the valve as described is balanced. In order to balance the valve with respect to its orts 57 and 58 so that the Ipressure ofthe. aid will in no way tend to cause the valve to be forced-to one side or the other, I provide the balance grooves 63, 64, 65"and66 formed in the outer periphery of the valve, the two balance ports 63 and ,port 35 is properly disconnected 64 being each equal in width to one-half the widthof the port 58'and of a circumferential length equalto the circumilerential lengtlrof the port 58 and symmetrically arranged wlth reference to a center line passing through the port 58, the two balance ports 65 and 66 being similarly arranged on the opposlte side of the valve and similarly roportioned with respect to the port 57. he balance orts 63 and'6 l are connected to the .ort 58 y suitable holes 67 and 68, and t ie two balance ports 65 and 66 are connected to the port 57 by the holes 69 and 70 drilled through the body of the web 350 1n such a way as to prevent improper communication between them. Formed in the inner wall of the crank chamber 34 are'subsidiarybalance ports 71, 7 2, 74 and 76 and the two ports not shown but similar to and in the same plane as port 71 and arranged in the same manner as ports 72, 74 and 76, diametrically opposite the respective cylinder ports 35, 36am 37, each of which subsidiary balance ports is one-half the width of'a cylinder port 35, 3-6 or 37, and has a circumferential length equal to that of such cylinder port, the subsidiary balance ports 72, 74 and 76 being in line with the balance ports 64 and 66 and the subsidiary balance ports 71 and the two ports not shown but corresponding to ports 7 4 and 76,; in line with the balance ports 63 and 65 of the main valve 56. Supposing pressure to exist in the pressure or outlet port. 58 'of'the valve, whichimplie s in turn that there is. pressure in the cylinder port 36, the valve would be subjected to a side ressure tending to displace it to the left in Iig. 5, the extent of the side pressure tending to thus displace it being determined by the width of the port 58 and the circumferential distance from the corner of the upper bridge 351 to the lower corner of the port 36, which in this case Would be 120 degrees. Since, however, the balance-ports 63 and 64 are connected to the port 58 they are also under the samepressure as the port 58 and since they circumferentiall overlap the subsidiarybalance port 74 an its companion port, not shown, to the same extent 7 the pert-5s overlaps the port36, the valve'56' isthereby subjectedto' a ressure tending to displace it toward theri t equal tothat'tending to 'dispiaceit tow r the left and it is, therefineflm balance: Sun'ilarl for other-positionsof the valve 56 the be ance portsof the valve co-actingwith the subsidiary balance pens" cause the valve to be always balanced, for when @the' port 5.3 is in communication with both the cylinder port 36and'the cylinder port 37 the balance ports 63 sneer are in an xact ly correspondin position I balance port's, 76andtl1e two correspon in port's, not shown, respectively.

intranet maintainthe main valve 56 with reference to the subsidiar of'the pump in its proper angular position with reference to the real crank both during rotation and adjustment of the length of stroke of the said crank, the said valve 56 is not driven directly by the crank shaft 40 on which it is mounted, but is driven through a connection with the eccentric bush 43 in a manner which I will now describe. Integral with the annular ring 54, see Fig. 1, is an eccentric 320, the center of which is coincident with the center of the exterior circumference of the eccentric bush 43. To the right of this eccentric 320 and integral with it is a second eccentric 321, the center of which, Where the parts are in the positions shown, is coincident with the center of the crank shaft 40; the annular ring 54 is counter-bored at its right end to bear on the crank arm 322, the circumference of which is concentric with the crank pin 41, the said crank arm merely acting as an additional support for preventing displacement of the annular ring 54. Mounted on the eccentric 320, and more clearly seen in the enlarged view Fig. 7. is a shoe and mounted on the eccentric 321 is :1 similar shoe 324. To the right of these eccentrics in Fig. l is a circular plate 325. terminating in a tubular sleeve 326 in which is a bushing 32? in which the crank shaft 40 is jonrnaled. The end of the sleeve 3526 is rigidly fastened to the inain valve 56 so that thesaid valve always moves with the said sleeve. In the left face of the circular plate 325 is a vertical slot 328 made equal in width to the width of the shoe 323 surrounding the eccentric 320 and in depth equal to the thick ness of the saidshoe. Formed in the same plate and per endicular to the said slot 328, but in a di erent plane, is a slot 329 made equal in width to the shoe 324 mounted on the eccentric 3:21, the said shoes 323 and 324 being slidably mounted in said slots 328 and 3 29. If the crank shaft 40 for the momentbe considered stationary and the eccentric bush beadjusted in a clockwise direction, as viewed from the left hand end of Fig. 1, the eccentric 320will cause the shoe 323t-o press against the sides of the slot 328 in the plate 325, and thereby turn the said late in the same direction. The said plate, li'riire'vcr, will not turn as rapidly as the said'eccentric bush, its speed of adjustment being only one-half that of the said bush.

In Fig, 8, drawn to the, same scale as Fig. 1, 1 have shown the eccentric 320 which is concentric with 'the exterior circum erence of the eccentric bush 43 and turns at the same rate that it-does) as adjusted through 90 in a clockwise direction from the position shown in Fi .7, audit will be seen that the slot 328 whic was vertical has not rotated through 90 but through only 45. In Fig. 9 theeccentric 320 has been rotated through 180 froin its position in Fig. 7 'and the slot 328 in the plate 325 has rotated through only 90. Similarly, in Fig. 10, while the eccentric 320 has been rotated through 2&0 the plate 325 has been rotated through only 120, and since the valve is rigidly connected to the said plate 325 by means of the sleeve 326, the said valve has only been rotated one-half as fast as the eccentric 3:20. and consequently only one-half as fast as the eccentric bush 43. The object of the second .ecccntric32l is apparent in Fig. 9, where the eccentric 320 having arrived at the position where it is concentric with the plate 325 is not in an advantageous position for causing further movement oi? the plate 325, but the eccentric 321, which in Figs. 1 and 7 was concentric with the crank shaft 40 and with the circular plate 325, has now reached its position of maximum eccentricity with reference to the said shaft 40, and, therefore, it is in its most advantageous position for causing its shoe 324 to turn the plate 325. It is apparent that as either eccentric moves from its position of greatest advantage for turning the plate 325 the other one moves toward its most advantageous position and at no time is there any difiiculty in the combination of the two eccentrics causing the plate 325 to be adjusted at its proper speed of one-half the rate of adjustment of the eccentric bush.

Referring again to Fig. 7 a is the main center of the pump and of the crank shaft 40, b is the center of the crank pin 41. and of the eccentric bore in the bush c is the center of the exterior circumference of the eccentric hush 43 and of theeccentric 320, d is the center of the exterior circumference of the eccentric 3:21, and the real throw of the crank, so far as the reciprocation of the pistons in the cylinders is concerned, is the distance from a to c. In the preceding description I have stated that the main "alve 56 :is maintained in its proper angular. osition with reference to the real crank o the pump, and I have also shown how the said valve 56 is adjusted at only one half the angular rate that the eccentric bush .43 is adjusted. Since, however, the valve fifimustact-toconnect the pump cylinderstorthe proper side of the fluid connection at the same point in the cycle, no matter what the length of stroke of the crank, the said valve 5-6 must always .be maintained .in its same angular position with reference to the real crank. Referring nowto Fi s. 8, 9 and .10, it will be seen .that in the adplstment of theeccentric bush 43 the real crank and the'valve do move together, for the real crank being the distance from a to c and its direction in line from a to a, this line a .to 0 is always maintained parallel to thesides of the slot 328 in the plate 325. It should be noted, however, that in Fig. 9, owing to the rotation of theeocentric 320 tl rough l,-.the center a has been brought to :Gfllfkflflzdfi with the center a, and therefore there 18 110 realerank, the eccentnic 3 en therefore, the outer ciroun rference of the occentric ib-ush being new concent ic with the center of the crank .shcilit 40. In this position there is consequently no reciprocation of the pistons in the pinup cylinders.

Further rotation of the eccentric 320 immediately causes the center 0 to pass from its position of coincidence with the center a and, as a result, the eccentric 320 and consequently :the outer circumference .of the eccentric bush is no longer concentric with the crank shaft 40 and consequently the real crank again has stroke and the pistons are, therefore, caused-to mfiiiprocate by the rotation of the shaft 40, Fig. 10 showscne such position where (the center 0 has passed through the position Where it is coincident with .the centerc to a position on the other side of the center a. The path of the center c is shown in Figs. 8, Qand '10 @by the curved line consisting of dashesund dots and it will be readrl y seen that this path is a circle drawn with the center b as .a center, the radius being the distance between a and b. It should also be noted that while the center 0 always remains in the diametrical line drawn on the circular plate 325 parallel to the sides of the Slot 328, yet that, in passing through its position of coincidence .with the center a. the said center a -.by-thc;act ofjpass mg throughthecenterc changes its angular position with reference to rainy point on the said diametrical line 1 80 degrees asa'eckoned from the said center a; .this is clearly seen by a comparison of F'gs. 8 and 10;, where in Fig. -8tl1e center 0 is to theright of the center a and in 10 it is to the left. Since the center a is the center of the real crank, it is, therefore, readily seen that in the adjustment of the stroke of the crank, thecrank instantaneously shifts its angular position with refereneetmthe circularplate 325 .when the said crankpasscs through the p n f :zero stroke, and in th ma n valve .56 r is rigidly .connected to the plate .325 this shifting of the said crank with refer.- ence to;thesaid plate,is also ashiftingef the crank with reference to the .main valve .56. i In order to (keep the .scale .of draw- 111 s as large .as possible the {InqtQr which ut1lizes .the fluid pressure generated in the pulnp 1S notshownon the same sheet, but both fluid Connections and mechanical connections .to the ,pumpgre shown as-broken ofl onthe right hand -;end.of the pump in '%he .motor,,a central longitudinal section of which is shown in Fig. 2, iSyllBIB ,represented asia partiel .duplicateofthe pump so far asthe latter has beendescribed themarts of it which are similarto-those in.the pump and designated by corresponding numerals naled. in a bearmfifis, hetweeniwhrch g re,

with an accent, the c linder 31 of the motor corresponding to t e cylinder 31 of the pump and similarly for the pistons, connecting rods, crank shaft, yalve, etc. In the motor, however, the crank is shown as of fixed length of stroke, the crank in 41' beingformed integral with the cran shaft 40, and the annular rings 53' and 54, which maintain the pitman rods 14, and 46 in contact with the crank pin 41 are fastened to the said crank pin 41 by the screws 353'. The pipe 62' which conveys fluid t0 the motor is connected to the outlet or pressure pipe (32 of thepump and the pipe which con veys fluid from the motor is similarly connected to the inlet pipe 60 of the pump, so that fluid under pressure may be delivered from the pump to cause the motor to re. volve and fluid which is forced, out. of the motor 0 linders as its pistons erform their outwar stroke is returnedtot e pump, the fluid thus being circulated from the pump to motor in repeated cycle. While I have shown the motor as a practical duplicate of the pump except for the adjusting mechanism for varying the len h of stroke,'it is to be understood that I 0 not limit myself to any particular type of motor, but prefer the type shown.

In the previous description of the pump the eccentric bush 43 'has been described as bein provided with, a bore by means of Whic it is mounted on the crank pin 41 and it -has been shown that where the eccentricity of the bore of theibush with reference to its exterior circumference is made. equal to the eccentricity of the cran Pi with respect to the crank shaft, by turning the eccentric bush on the crank pin, the eccentricity of the exterior circumference of the hush with respect to the crank shaft may be made anything between twice the eccentricity of the pin with respect to the shaft, and zero. In the first case the eccentricities are added together and in the latter case they exactly neutralize each other, and ,in between these limits the eccentricityof the outer circumference of eccentric bush.

is an exact function ofthe angular distance between the center line joining the center of the crank in to the center: ofthe crank. shaft and the center line oini'nghthe. center of the outer circumference of t e bush to the center of its-eccentric bore,=

In order to ang'nlarly adjust theeccen tric bush on the crank pin whil e latter is in motion and to hold it inwhatever'pw sition it has been ad usted, the'fo'llow ng means are provided: Mounted on the, crank shaft 40, Figs. land {1, isa; sleeve 7?? ours and thecrank s aftisinserteda tuhnlar bushing 78 The sleeve 77 terminates atiits,

right hand end In an integral circular plate '79 provided with a diametricalslot 8 0,.

Formed in the adjoining end of the eccentric bush 43 and in its integral annular ring 53 is a diametrical slot 81 snnilar and at ri ht angles to the slot 80 in, the late 79; t is slot 81 is formed centrally wit l. respect to the bore of the eccentric bush and perpendicularly to the line which joins the center of the bore to the center of the periphery of the bush. Interposed between the late 79 and the eccentric bush 43 is a circuar plate 82 provided with a tongue 83, fitting into, and free to slide in, the slot 80, while on the opposite face of the said plate 82 and'at right angles to the said tongue 89 is a tongue 84, fitting into, and free to slide in, the slot 81 in the end of the eccentric bush, the said arrangement of tongues, slots and plates constituting; what is popularly known as an Oldhamcoupling which is a well known means for connecting two parallel shafts in different planes. Mounted on the crank shaft 40 at the other end of the sleeve :77 is the adjusting device which efi'ects the movement of the eccentric bush on the crank. pin, and which will now be described.

Referring to Figs. 1, 11, 12, 13, 14, 15, 16, 17, 28 and 29, 90 designates a circular plate in each face of which are formed two circular gmoves, an inner groove 91 and an outer groove 92 in one face, While in the opposite ace is anxinner roove 93 and an outer groove 94, the sai late being fastened to the crank shaft 40 y means of akey-95, F ig. l5. Loosely mounted on the crank shaft 40 between the plate 90andthe sleeve 77 is a circular plate96, terminating on one side in a boss 355 by means of which it is connected to the sleeve 77 'b a pin 97, and terminating on the other si e in an annular ring 356 which surrounds and rojects beyond the said plate 90. Formed in the interior face of the plate 96 is an inner circular groove 98 matching the groove and an outer circular groove 99 matching the groove 94. Mounted in the interior of the annular ring 356 in which the plate 96 terminates is a circular plate 100 in one face of which is formed an inner circular groove -101 matching the groove 91 and anouter circular groove 102 matching gtlie groove 92, the above described grooves being, each shown .as semi-circular in section. whereby each pair forms a circularchannel. Mounted i the circular groove 101is a piston 103 which projects into the groove tll, while facing this piston andJnounted inthe roove 91 is a piston 104 which rojectsinto t is roove 101, thepiston 109 being fastened tot e circular late 100 by apin l05,while the-pist n 04 15,- fastenedto the plate 90 by,

apin .106. Fastened into the outer. roove,

1021by a ,pin 107 is ,a piste 10.8 wine 1 pro -i,

ton 110 being dimnetricelly opposite the piston 10 1111111 the piston 108 being diihuctrically opposite the piston 103. Fastened in the groove 98 of the plate 96 by n pin 111 is a; piston 112 which projects into the groove- 93 of the plate 90 and fastened in the groove 93 by a pm 1513 is a. piston 114 which projects into the groove 98 while fastened in the more 99 by a pin 115 is a piston 116 which projects into the grc'rove 94- and fastened into the groove 94 by a pin 117 is :1 piston 118 which projects into the groove 99, the: said piston 116 being di'mnetrically opposite the piston 112 and the piston 11.8 ban dist-metrically opposite the piston 114. The plate 160 is fastened into the annular ring 356 of the pltt'te 96* by means of a, pin 119 and the nuts 1'20 and 1'21 which are threaded into the said annular ring. Fustened to the crank shaft 40 by the pin 1252 is a circular plate 123 which terminates in an aflnuhir' ring 124, projecting over and surrounding the annular ring 356 of the plate 96. F armed in the outer eircui'nfeience of the annular ring 356, diametrically opposite each other, are two longitudinel slots 12:3 and 126, Fig. 12 extending pm'tinllv through the body of the ring. Formed in the circumference of the annular ring 121- are two diametrically opposite spiral slots 127 and 128, extending entirely through the 1 d of the "annular ring, find mounted in the ion itudinall slot 125 is a block 129 on the outer ace of which is formed it pin 1'30, passing through the spiral slot 128 in the annular ring 124. Similarly, in the slot 126 is a block 131 (ffittlie (filter time of Which1 is a in 132, so in' t 'roug tie spiral s ot 1% iii th mnuhi r ring" 1E4. Slidahl v mounted on the rin" 124 is a ring 133 on which is a. shoulder 31 and mounted on this ring is a. second ring 135 which is secured thereto b? means of the )ins 130 and 13% passing through the spire. slots in the unnular ring 12 1. Mounted on the ring 1331 and between the shoulder 134 and the ring 135, is a ring 136, for convenience here called the yoke, which is shown (is slightly larger than the ring 133 for reasons hereinafter described, in which ring 136 are two holes 137 and 138, diametrically opposite each other in which are mminted' pins 139 and 14-0. tospectiv'ely, the said ins serving to connect the ring-like lever 151 to the yoke 13%. At its lowerend the lever 141 terminates in st hollow lug 142 in Which is mounted a block 145, seci'lred thereto the pins 143 and 144, which block 145 is ttl'so' secured to a 0011 I01 rod 146 between shouiders 14-7 and 148, w lie the rod 146' is s'lidehljf mounted on one side in a bushing 149, F lg. 1, fastened into the casing 150, :1nd, on the other side, in a bore 151 formed in ft boss 152, projecting non-1 the crank chamber 34. The up er end of the lever 141 is similarly connected to the valve rod 153, provision for a slight vertical movement of the block 15-1- between the shoulders of the valve rod 153 being nurde. From the above description it will be readily seen that if the fluid pressure is admitted. between the proper heads of the pistons mounted in the circular grooves in the plates 96, 90' and 100 such fluid pressure will cause the plates 96 and 100 to be rotated with reference to the plate 90, the extent. of such rotation bein dependent on the amount of fluid admit-ted, and since the plates 96 and 100 are connected to the eccentric bush 43 by means of the sleeve 77, the pin 97 and the (lldlutfu coupling and the )late 90 is connected to the crank shaft 4- hy the key 95, such rotation of the plates 96 and 100, with reference to the plate 99, will cause the eccentric bush 43 to be rotated around on the crank pin 41 end in order, therefore, to

utilize this mechanism to perform adju tments of said eccentric hush, it is only neccessary to provide means for permitting part of the fluid pressure generated in mi pump to pass into the circular channels just described in order to cause the power of the pump to effect the? adjustment of its stroke. The further provision of nn'un's for controlling the admission of fluid from the pump into the adjusting mechanism and from the adjusting mechanism back into the pump furnishes means fol-properly controlling the said adjusting mechanism. The means by which this fluid pressure is admitted under proper control to the said circular channels to olqerate this adjusting mechanism will be later described.

If all the ports and passages and the cylinders of the pump and the motor and the pipes connecting their] are completely filled with u )l'flCtlCztll) ineompressihle fluid, such as oil or writer, and there was no leakage, after these spaces had once been filled. it would not be necessary to supply further fluid to the fluid connectioin but since rectical considerations make it necessary t iatthere be a certain amount of leaka'g'e es 'eeielly around the pistons and valves into to interior of the crank chambers I find it advantageous to use sum 1 leakage pump which picks up the fluid leaking into the crank chamber and returns it to iho fluid connection between the pump .LlKi motor. At the left hand end of Fig. 1 is shown such a pump 240, which may he of any form desired but is here shown as of the c onveir tional gear type and supported from the hub 175 by the brackets 241, which are secured thereto by screws 242; the pump is driven by the shaft 40 through the key 243, and a pipe 244, here shown as broken, is con nected at one end to the suction side of the said gear pump, its other end being connecte to the interior of the casing 150, and enters the casing at the bottom through a plu 245. Connected to the delivery side of 510 gear pump 240 is a pipe 246, communicating through a pipe 247 with a pipe 248. Formed on the lower side of the pipe 247 is a chamber 249, closed by a cap, 250, muimunication between the ipe 247 and the chamber 249 being normal y prevented by the valve 251 held in place by a spring 252. Connected to the side of the chamber 249 is a pipe 253, the other end of which is con nected with the interior of the casing 150.

Formed on the upper part of the casing 150, as viewed in Fig. 1,.are three valve chambers which with their valves and connections constitute the means by which fluid pressure from the pump is utilized to operate the adjusting device for varying the stroke of the pump, and also the means. for insuring that the leakage pump will keep the main circuit full of fluid. Of these three valve chambers, the lower one parallel to the axis of the crank shaft 40 is designated the adjusting valve chamber, the upper left hand one 254 is designated the circuit valve chamber and the upper right hand one 255, the pump valve chamber. In Fig. 1 it will be clearly seen that the pipe 248 is connected to the boss 256 on the side of the said pump valve chamber 255. Gonneoted to the boss 257 on the side of the circuit valve chamber25 is a pipe 260. the ot iereiid of which is connected with the main circuit ipe 62. Behind the boss 257, as viewedin ig. 1, is a boss 259, see Fig. 20, to which is connected the pipe- 258, the other endof which is connected to. the main circuit pipe 60. Itwill thus be seen that the leakage pump is directl connected to the pump valve chamber an thatthe circuit valve chamber is directly connected to both sides of the main circuit through which the fluid circulates bet-Ween the pump and the motor.

Slidably mounted in the adjusting valve chamber 160 is the adjusting valve 161. shown more clearly in thelongitudinal sectional wiew in Fig. 2.0,:vwhere ittwill' be .seen that said, valve terminates at its left hand endin a valve stem 153, bywhich itis con nected to the adjusting yoke 141,; as prevj ously described, the

I bloclrv being; hel d between the; shoulder 162 andthe tubular bushing 163,, held place ion the, .valve rod.

or stem 153 by-a nntilfie i sohas toprevent longitudinal motion of the block 154; on the rod 153,. but to permit a slight vertical motion with reference. thereto reason of tieclearance between the said block 154 and the rod, 53,,Fig. 20. kThev-alve 161 comprises va ye heads H and in the valve; chamber 160.,arevports 17,0 and 171 ere shown ascovered by t 'e valve. heads 16 and ,167, respectively,' between Whtlfr tWQPOltS,EIS Q p'qrt172.

.1 eferr'i'ng newimeremaitulan a rig;

18, Sheet}, the crank cheer- 165,166, in, i'fihand its;

ing in a bushing 170,;aspllt collar 177 with its inclosing ring 178 preventing longitudi; nal motion of the shaft 40 toward the left. Tightly mounted on the exterior of the shaft is a bushing 170, the right hand end of which adjoins the end of the bushing; 176. The hub is countcrbored, and fastened against the end of the bore by pins .180 is a ring 181. Surroui'iding one-half the length of the bushing 17%) is a bushing 182 having a collar 183 which fits against the ring 151. while fitting against this collar is a ring 184 mounted in the bore of the hub 175. Surrounding the other half of the bushing 179 is a bushing 185 having a collar 186 fitting against the ring 184, and fitted against the opposite side of the collar 186 is a bushing 187, mounted in the bore of the hub 175. 187 terminates in a threaded ring 188, whose threads fit threads formed in the interior of a ring 189, secured by suitable means, to the end of the hub 175. Formed in the interior of the ring 189 at its outer end are screw threads into which is fitted :1. ring 190 and in the outer end of the said ring 190 is a soft washer 191, serving to prevent dust from entering the bearing. Mounted in groove192 in the shaft 4-0 is a split ring 193 With its inc-losing ring 194, acting as a thrust collar to prevent longitudinal motion of the said shaft 40. Mounted in the bushing- 187 is a bushing195 in which the shaft 40 is journaled. "Formed in the shaft 40 near its center and parallel to the axis thereof are two channels 200 and 201, respectively, the channel 201 being; connected by the approximately radial holes 202 through the shaft 40 and the bushing 179 with the radial holes 203 through the collar 183 of the bushing 182, the said bushing 182 being provided with a counter bore 204. the width of which, for reasons hereinafter explained. is made equal to the Width of the said collar 183, the said counter-bore maintaining the said holes 202 and 203 at all times in communication even. when the shaft is rotating. Siniilarlythe channel200 in the shaft 40 is connected by means, of the radial holes 205 and the counterv bore 206v with the radial holes 207 through the collarlt 0f thebushs i-ng :-185, FOI[l1Gd il1: the .hub 175. is. a chum nel 208 the upper end of which is not shown, but which passes through the wall of the cas inn 150 up to the adjusting valve chamber 160. Figs. 1 and 20, and is the're connected to the port 170, thereby connecting said port,

170 through the radial holes 203 and 202 ivitlrthe channel 201v of the shaft 40. In a similar manner tzhe rham el 209 formed in tliehub 175 and the casing 150,- the upper end of which is-not shown, passes up through the wallof the ,saidcasingdnto the port 1710f the adjacent valve chamber 160,

saeiFigs, 1 and 20, and there conneets the.

The bushing iii? as through as in port 171 of the zuljusting valve-chamber 160 with the radial holes 207 and thence through the radial holes 205 in the shaft 40 to the channel 200. Referring now more particularly to Figs. 1, 15, 16 and 17 the channel 200 is connected by the approximately radial holes 210- and 211 in the shaft 40 with the approximately radial holes 21 2 and 213, respectively, in the circular plate 90 which, as previously described, is fastened to the shaft 40 by the key 95. The radial hole 212 iinall y connects through the axial hole 214 with the two outer circular grooves formed in the faces of the circular plate 90, the said axial hole 214 entering the groove 92 between the piston heads 1'10 and 108 on one si le of the circular plate 90 and entering the other circular groove 94 between the piston heads 116 and 118. The radial hole 213 is connected by the axial hole 215 with the inner circular groove 91. between the piston heads 103 and 104. on one side of the plate 90, and on the other side thereof the said axial hole 215 connects with the inner circular groove 93 between the piston heads 112 and 114. In a similar manner the channel 201 is connected through the radial holes 216 217. and the axial hole 218 with the outer circular channels 92 and 94 at a point just beyond the respective piston heads 110 and 118, and through the radial holes 220, and 221 and the axial hole 222 with the inner circular grooves 91 and 93 at a point just beyond the outer ends of the respective piston heads 104 and 114. If the port 172 in the adjusting valve chamber 160 is conneoted with a source of fluid pressure supply and the ports 226 and 227 are connected to some chamber into which they can exhaust fluid, it will be readily seen that if the adjusting valve 161 is moved toward the right in Fig. 20 to a suflicient extent to uncover the port 171, fluid pressure will pass into the port 171 thence through the channel 209 formed in the casing 150, thence through the radial holes 207 and 205 into the channel 200 in the shaft 40 (Fig. 18) and thence through the radial holes 210 and 212 and the axial hole 214 into the circular groove 92 between the piston heads 108 and 110, and between the piston heads 116 and 118 in the groove 94. and at the same time fluid will also pass through the radial holes 211 and 213 and the axial hole 215 into the inner circular grooves 91 and 93 between their respective piston heads 104 and 103 in the circular groove 91, and 112 and 114 in the circular groove 93. Fluid pressure thus being permitted to pass between the piston heads will cause the circular plates 96 and 100 which are fastened toge her to be rotated in a counter clockwise direction, as viewed from the left hand end of Fig. 1, and such rota tion of the said lates by their connection 7, sleeve 77 and the Oldham coupling will cause the eccentric bush to be rotated in a counter clockwise direction onthe crank pin 11. 11 there be fluid in the inner circular channels between the outer ends of the pistons 103 and 104 and the pistons 112 and 114, or in the outer circular channels between the outer ends 01' the pistons 108 and 110 and the outer ends of. the pistons 116 and 113, anamount of fluid will pass out of each cirel-rlar channel, through its connection with the axial channel 201 in the shaft 40, equal in volume to that admitted under pressure between the inner ends of the pistons in their respective circular channels and the fluid so passed into the axial channel 201 will be free to pass through the radial holes 202, 203, and

the channel 208 formed in the casing 150 into the port 170-, and since at the same time the head 167 of the adjusting valve 161 uncovered the port 171 and thereby connected it to the port 172, the port 170 was uncovered by the head 166 and thereby con nected with the port 226. such fluid so passed to the port 170 will be free to pass through the port 226 and into any receptacle provided therefor. In a similar manner. it the adjusting valve 161 is adjusted to the left in Fig. 20 so that the port 172 is connected to the port 170, fluid under pressure will pass in the opposite direction into the circular channels of the adjusting device and thereby cause the eccentric bush 43 to be adjusted in the opposite or clockwise di reetion as viewed from the left hand end of Fig. 1. In Figs. 1, 11-17 the adjusting mechanism is shown with the pistons at the extreme limit of their clockwise direction of adjustment, so that clockwise adjustments are only made when they have been dis placed by counter clockwise adjustments from the positions shown.

It is furthermore evident that, if the adjusting valve 161 is adjusted toward the right in Fig. 20, whereby fluid pressure causes the circular plate 96 to be adjusted in a counter clockwise direction, as viewed from the left hand end of Fig. 1, the ring 133 mounted on the exterior of the annular ring 124 will, through the plate 129 and its pin 130 co-acting with the axial slot 125 in the periphery of the annular ring 96 and the co-acting spiral slot 128 in the ring 124 and the similar co-acting and corresponding parts diametrically opposite thereto, cause the said ring 133 to be displaced toward the left and to an extent depending on the pitch of the spirals 127 and 128 and the extent of the an lar counterclockwise motion of the said a justing device. Such motion of the ring 133 will cause the yoke 136 to correspondingly move toward the left, and thus the yoke 136 will, through its connection with the adjusting lever 141 cause the ad justing valve 161 to be moved toward the left, the lower end of the said adjusting lever 141 which is connected to the control rod 146 being supposedly held by the operator and prevented from longitudinal motion. Since the counter-clockwise adjustment of the adjusting device was produced by the adjusting valve being adjusted to the right in Figs. 1 and 20 and since such counter-clockwise motion of the adjusting device caused the adjusting lever to move the adjusting valve toward the left and since inverse adjustments of the adjusting valve will cause the adjusting device to so move the adjusting lever as to cause the adjusting valve to be replaced in its normal or neutral position Where the ports 170 and171 are both covered by their respective valve heads and since, by manual adjustment of the rod 146 the adjusting lever 141 pivoted to the yoke 136 by the pins 138 and 139, and the adjusting valve 161 can be adjusted in either direction and the adjusting mechanism thereby caused to adjust the eccentric bush 13 in a corresponding direction and to a corresponding amount till the motion of the adjusting mechanism has caused the adjusting valve 161 to be replaced to its normal-or neutral position, and it is obvious that such a combination of mechanism provides means for causing fluid pressure to adjust the cocentric bush 43 and thereby to vary the throw of the crank of the pump to an extent determined by the extent of the manual ad j ustment of the said rod 146. It is to be particularly noted that the above descrlbed mechanisms not only cause the stroke of the crank to be adjusted simultaneously with and to an extent corresponding to the manual adjustments of the rod 146, but that as soon as the said mechanisms have effected such adjustments of the stroke of the pump crank they act to lock the stroke at the point arrived at, since any extraneous movement of the eccentric bush after the adjusting valve 161 has been returned to its neutra position would involve the impossible function of forcinv fluid through ports and passages which iiave been closed by the said ad usting valve.

In the foregoing description of the ad justing mechanism it has been assumed for simplicity that a source of fluid-pressure Suppl was connected to the port 172 and i that t e fluid exhausted from the adjusting mcchanisn'i was free to pass out of the ports 226 and 227 into some receptacle provided therefor; since, however, the pump'itself is capable of furnishing a fluid pressure sup ply for operating the adjusting mechanism I provide means for properly seouringthis fluid pressure supply or the adjusting mechanism from the pump itself, such means consisting, in thepresent instance, of

the three valve chambers 160, 254 and 255 and their valves and connectionspreviously I formed in t e referred to. Referring now more particularly to Figs. 20, 21, and 22, from a detail illustration of these means, it will beseen that a circuit valve 261 comprising three heads 262, 263 and 264, isslidably mounted in the valve chamber 254..

Closing the left hand end of the valve cha1nber254 is a recessed plug 265 in'ivhich is mounted a stop-rod 266, adjustably scoured to the said plug by threads 267 and a nut 268 and extending a considerable dis tance into the valve chamber and passing into a hole 269 in the stem of the said valve 261. The head 262 is counter-bored to receive a compression spring 270, confined between the said head 262 and the plug 265, which normally pushes the valve 261 toward the right and against a stop "27 5 on a plug 276 closing that end of the valve chamber. Mounted in the pump valve chamber 255 is a 8 pump valve 271 comprising three heads 272, 273 and 274:, respectively. Closing the left hand end of the pump valve chamber 255 is a plug 277 in which is mounted a stop rod 278 adjustably secured to the said lug by screw threads 279 and a nut 280. urrounding the rod 278 is a compression spring 281, confined between the valve head 272 and the plug 277, and normally causing the pump valve 271 to be forced to the right till the head 27-1 is against the stop 282011 the plug 283, closing that end of said valve chamber. Formed in the circuit valve chamber 254 is a port 285 connecting with the boss257, with which the pipe 260 is connected as previously described. Formed in the same valve chamber 254 is a similar port 286C011- necting through the boss 259 with the pipe 258 previously described, the pipe 258 thus connecting the valve chamber 254 with one side of the main fluid circuit and the pipe 260 connecting it with. the other side thereof. Leading from the port 285 is a small channel 287 which connects with the port 288 in the left hand end of the circuit valve chamber 254, a similar channel 289 on the right hand side connecting the port 286 with the port 290. Mid-way the length of the circuit valve chamber 254 is a narrow port 291,

which, by means of the channel 292,flS C011' by a channel 296, morezclearly seen in Fig. 22.

In the pump valve chamber 255 near the right hand end is a port 297, connectedby a suitable channel, not shown, with the hlgh pressure su ply' port 172 in the adjusting valve cham er 160, the said channel which connects the 1port 297 with the port 172- being lower, side Wall of the said valve chamber, 255. Near thc port in the pump valve chamber 255 is a pod; 298, connected by a channel 303 with the port 299 ofthe adjusting valve chamber 160, the said channel 303, formed in the side wall of the adjustin valve chamber 160 and passing along 1: e same till it reaches the pump valve chamber 255, when it nmkos a right anfile bend and passes along the bottom Side wal of the said valve chamber 3511 till it reaches the said port 298, which it. enters, and ort 299 being shown in dotted outline in Fig. 21 and thesaid port 299 being shown in Fig, 2011s a dotted circle. Adjoining the port 298 in the pump valve clnunbcuZfifi is a port 300, which coni'iects through the boss 256ivvilh the pipe 248, and thence with the delivery side of the leakage gear pump 240, previoi'isly described. Adjoining the port 300,. on the other side from the port 298, is a port SOl which connects through the channel 302 with the channel 296, which connects the port 294- to the port 2 5, and. duringjthis course, crosses the chamber 160 through which it passes at the port 226, and t.lience' finally by means of the channel 5305 with the ports 994 and Ll- 5 of the rin-ui: valve chamber 954 and with the ports 22'; and 227 of the adjusting valve chamber 160 It will be noted that the port 226 is lornuwl by the intersection of passage 296 with the bore of adjusting valve casing 1'60, and pas sage 306 connects port; 227' in the casing 160 with p assa 296 and hence with the bore of easing 1 0 at the so-called port 226.

In the stem connecting the pump valvr heads 27? and 273 is a radial hole film-coni'i'ectingftlirou an axial hole 325 in the said valve Wit the radial holes 305, in the Stem between the valve heads 273 and 27- In Fig. 22 the middle circle, situated be tween the channel 306 and the channel l i"? represents the bore of the adjusting valve chamber 160 which, it should be lt lllmlh bored, lies in a plane below and with it axis perpendicular to the axes of the circuit valve and pump valve. Closing the right hand end of the adjustinc valve chamber 160, Fig. 20, is a plug 30 In the upper portion of the casing 150, Fig. 22, is a mall chamber 309, normally closed against the channel 296 by a valve 310 held in place by the sprin 3-11, which, .for reasons hereinafterex atined, is' so adjusted that the valve dens when the pressure in the chamber 296 r! es to some predetermined amount above atmospheric pressure. The stem oi the va'lh'e 3T0 is u'ided by a gland 312 in which are formed 'oles 313 to permit fluid to pass from the chamber 309" into the interior of the casing 150 Leading from the port 299 in the right hand end of the adjusting valve chamber ftil) and between the heads 1'68 and 169 is a channel 314, Fig. 21, which connects with the channel 306, as previously explained connecting with the channel 296 and thereby with either the port .285 or the port 286, dcpen'dihg on the position of the circuit valve 261.

This systcn'i of valves just described is so interconnected through the channels and ports that the circuit valve 261 will, when pressure exists in the main circuit between the pump and the motor, maintain 21 suppl of fluid pressure in the port 172 of the ad justing valve and at the same time maintain a connection between the ports 226 and 227 of the adjusting valve and the low pressure side of the main fluid circuit. When there i:-: no supply of fluid under pressure in the main fluid circuit bet-ween the ump and themot'or, as whemt'he'pump cran ll has been adjusted to zero stroke, the pump valve 271 will automatically shift to such a position as to enable the port 1 72 to be supplied from the leakage pump'240, with fluid under a sulhcient pressure to operate, should the operator so desire it, the adjusting mechanism suthciently to adjust the pump crank from zero to a position Where it has stroke and therefore where there is again pressure in one side or the other of the main fluid circuit.

Referring to Figs. 1, 3 and 25, it will be seen that in the head of piston 50 there is a hole 360, in which is slidably mounted a tube 361, terminating at its lower end in a crescent shape shoe 362, which fits around and bears on the rounded end of the pitman rod 44; the bore 363 of this tube 361 terminates at its lower end in a recess 364. Drilled throu h the pitlnan rod 44 from end to end is a be e 365, connecting, at its upper end, with the recess 364 in the shoe 362, the said hole 365 terminating at its lower end in a recess 366 formed in the bearing surface of the pitman rod 44 where it bears on the exterior of the eccentric bush 4:3. Formed in the bore in the upper end of the pitnian rod through which the piston pin 17 passes, is a couuterboreil groove 367, connecting together the two portions of the hole 365 where it is interrupted by the pin 47. It will be seen from Fig. 25 that the recess 3-66 in the bearing surface of the pitman rod 44' is entirely surrounded by a groove 368, and this groove 36'8is conn'ected to the outer periphery of the bearing surface by the several grooves 369'. The area of the recess 366- projected onto a plane perpendicular to the length of the pitman rod 4 4, is preferably made equal to a considerable fraction of the areaof the piston 50, and the projected area which is inclos'ed by the surrounding groove 368 is preferably made just equal to or slightly less than the area of the piston 50, for, when such is the case, a slight amount of the fluid pressure generated in the pump cylinder 31 will be free to pass through the who 361, pitman rod 4*? and into the recess 366, where it will pitman rod is equal toor area of the piston so cess 366 to whichithey are recess 366 with preventing leakage of f .ried from between, the bearing spread out over the area of the recess 366, and thereby relieve the bearing surface of the pitman rod 44, where it bears on the eccentric bush 43, of a certain portion of the bearing pressure due to the fluid pressure acting ontop of the piston 50, the percent age by which this hearing pressure is re lieved being an exact function of the projected area of -the recess 366, for if tween the pitman rod andfthe bush, it is readily seen that the friction of the mechanism will be greatly reduced. I prefer,

owever, not to make the recess 366 quite equal in area to the sure penetratesto a certain extent this surface and the surface of the hush 43, and thereby tends to lift the pitman rod from its bearing, and thus permit fl'uid pressure to leak out of the recess. '1, therefore, make thevprojected area of the rea considerable fraction of the area of the piston, sothat the pressure-between the bearing surface of thepitman' rod and the eccentric bush is not entirely counteralanced, the pressure which is notcounteralancedi thereby holding the surface of the pitman rod tightly against the'surfaee of the eccentric bush and preventing fluid from leaking between these surfaces. Since, however, tween any two surfaces fluid prespenetrate to an extent depending he accuracy with which the surfaces fit and the extent of the pressure subjected, I surround this the. groove 368, which, as stated before, incloses an area which, when projected on a surface perpendicular to the on t each other that even though there be penetration o thefluidbetween the surfaces it will not be able to act on a surface greater in; area-than the area of the piston, thereby preventing the itman rod from being raised from the be and thus the fluid pressure rom the recess 366, the fluidipressure which penetrates between the surfaces and into the surrounding groove-368 being; carsurfaces hrou h the several grooves 369.

iig. 3 it will be elearhv that the v of the tube oil or some other of the crank chamber 34, and

nil-

shoe 362 in which lhe tube 361le|1ninates is pressed against the exterior surface of the pitman rod 44 by the fluid pressure acting on the upper end of the said tube 3,6 1 the extent of t e pressure between the shoe and the pihnan rod being dependent on the area of the recess 364 relative to the area of the end of the rod 361, the area of this recess being preferably made slightly less than the area of the end of the rod, as is shown in Fig. 26, which-isa plan view of the suw face of the shoe 36:2 whom the same rubs on the exterior surface of the end of the pitman rod 44; this recess is surrounded by a small groove 3'70 and the projected area in.- closed by th than the area of theuppe-r end 361, and such fluid as penetrates through the locking surface between the recess 364 and its surrounding groove 3 0 is carried from between the surfaces hv t e grooves 371, thereby preventing the shoe circuit between thepump fluid 111g qualities, a further very great advantage is also incidentally obtained in that the bearing surfaces which are subjected to the unbalanced pressure and which act as locking surfaces to prevent leakage of the fluid,

advantageous conditions; as

work under very when the flnidpres regards lubrication; for, sure is high and the pressure, therefore, correspondingly high, the fluid penetrates to a greater or less extent between the surfaces and thereby assists very greatly in the proper lul'iriration of these bearing surfaces. All of the other pistons and pitman rods are similarly equipped with the abme described means of conveying fluid pressure between the pitman rods and the eccentric bush. Similarly in motor, shown in Fig.2, corresponding parts and passages convey fluid pressure between the several pitman rods and the crank pin :41, and thereby. greatly reduce the frictionv between the ring surfaces of the pitma-n rods and the said crank pin 41. p The bearings 38 and 39 of the formed in them the small holes ting fluid to pass from one end pump have 373 permitto the other the corresponding bearings 38' and 39 of the motor are similarly provided crank cha-m er 34' of thefmotorfi bv ereby fluid leaking: into t unbalanced bearing ill) 

